FR3116765A1 - Heat treatment device - Google Patents

Abstract

Heat treatment device The present invention relates to a heat treatment device (3), comprising a first heat transfer fluid circuit (301) and a second heat transfer fluid circuit (302), the first circuit (301) comprising a main pump (71), a first heat exchanger (50) configured to operate a heat exchange between the heat transfer fluid and an external air flow (5), the second circuit (302) comprising a third heat exchanger (58) configured to operate a heat exchange between the heat transfer fluid and the external air flow (5), characterized in that the first heat exchanger (50) and the third heat exchanger (58) are side by side and extend in elongation planes intended to be crossed by the external air flow (5), said elongation planes being parallel to each other at +/- 2°. (figure 1)

Description

Heat treatment device

The field of the present invention is that of heat treatment systems used to heat or cool an enclosure or a component of a vehicle, in particular a passenger compartment or a component of a traction chain of this vehicle.

Motor vehicles are commonly equipped with a coolant circuit and a heat treatment device capable of circulating a heat transfer fluid. The refrigerant circuit and the heat treatment device are both used to participate in a heat treatment of different areas or different components of the vehicle. It is in particular known to use the refrigerant circuit and/or the heat treatment device to heat treat a flow of air sent into the passenger compartment of the vehicle equipped with such a circuit.

In another application of this circuit, it is known to use the heat treatment device to cool components of the traction chain of the vehicle, such as for example an electrical storage device, the latter being used to supply energy to an electric motor capable of setting the vehicle in motion. The heat treatment system thus supplies the energy capable of cooling the electrical storage device during its use in the driving phases.

Car manufacturers are constantly improving their vehicles. These improvements include structural modifications responding to customer requests, such as independence of the circuits forming the heat treatment device, each of the circuits being configured to perform its own function.

The present invention falls within this text and proposes a heat treatment device for a vehicle, comprising at least a first heat transfer fluid circuit and a second heat transfer fluid circuit, the first heat transfer fluid circuit comprising a main pump, a first heat exchanger heat exchanger configured to effect a heat exchange between the heat transfer fluid and an air flow exterior to a passenger compartment of the vehicle, and a second heat exchanger configured to effect a heat exchange between the heat transfer fluid and an interior air flow intended to be sent to the passenger compartment of the vehicle, the second heat transfer fluid circuit comprising at least one first additional pump, at least one second additional pump, and a third heat exchanger configured to effect a heat exchange between the heat transfer fluid and the flow of outside air, characterized in that the first heat exchanger and the third heat exchanger are have side by side and extend in elongation planes intended to be crossed by the external air flow, said elongation planes being parallel to each other at +/- 2°.

The first heat exchanger and the third heat exchanger being independent of each other, each of them is therefore in a circuit having its own function. This avoids mixing the heat transfer fluid of the two circuits within a single heat exchanger interacting with the outside air flow. In addition, the first heat exchanger and the third heat exchanger being placed side by side, the heat exchange taking place between the latter and the flow of outside air is identical. In other words, the first heat exchanger and the third heat exchanger are not superposed with respect to one another with respect to a direction of the flow of outside air. Furthermore, the first heat exchanger and the third heat exchanger can be side by side without necessarily extending along the same plane. Thus the elongation planes of the first heat exchanger and of the third heat exchanger can be parallel without however being coincident. The first heat exchanger and the third heat exchanger are advantageously strictly parallel to each other in order to both interact correctly with the flow of outside air. A tolerance of +/- 2° is however possible between the first heat exchanger and the third heat exchanger.

At the level of the first circuit, the main pump allows the circulation of the heat transfer fluid. The latter can thus circulate through the first heat exchanger to ensure management of the heat transfer fluid calories. The heat transfer fluid can also circulate to pass through the second heat exchanger in order to heat the interior air flow, which is then sent to the passenger compartment of the vehicle in order to heat it. As such, the second heat exchanger can for example be integrated within a ventilation, heating and/or air conditioning installation.

The second circuit comprises two additional pumps allowing the circulation of the heat transfer fluid according to several loops each responding to a specific function. The third heat exchanger also allows the management of calories between the flow of outside air and the heat transfer fluid of the second circuit.

According to a feature of the invention, the elongation planes of the first heat exchanger and of the third heat exchanger may coincide.

According to a characteristic of the invention, the first heat exchanger and the third heat exchanger can form a one-piece assembly. The one-piece assembly facilitates the layout of the first heat exchanger and the third heat exchanger. In order not to mix the heat transfer fluid circulating in the first circuit and in the second circuit, the one-piece assembly comprises a junction making it possible to separate the first heat exchanger and the third heat exchanger.

According to a characteristic of the invention, the first heat exchanger comprises an inlet mouth and an outlet mouth and the third heat exchanger comprises an inlet orifice and an outlet orifice, the inlet mouth being separate from the inlet orifice and the outlet mouth being distinct from the outlet orifice.

According to one characteristic of the invention, the first heat transfer fluid circuit comprises a main section starting at a first point of convergence and ending at a first point of divergence, as well as a first section and a second section which both start at the first point of divergence and end at the first point of convergence. When the heat transfer fluid is circulated in the first circuit, the heat transfer fluid necessarily circulates within the main section. Subsequently, depending on an operating mode of the heat treatment device, the heat transfer fluid is directed towards the first section and/or towards the second section.

According to one characteristic of the invention, the main section comprises the main pump and a fourth heat exchanger configured to effect a heat exchange between the heat-transfer fluid and a coolant of a coolant circuit. In order to ensure all the functions of a heat treatment system, the heat treatment device and the refrigerant circuit interact by heat exchange. This is particularly the case via the fourth heat exchanger. The latter allows the heat transfer fluid to recover the calories of the refrigerant in order to cool and condense the latter. Incidentally, the heat exchange occurring at the level of the fourth heat exchanger makes it possible to preheat the heat transfer fluid in the context of heating the passenger compartment afterwards.

According to a characteristic of the invention, the first section comprises the first heat exchanger, the second section comprising the second heat exchanger. In general, the first section makes it possible, for example, to dissipate the calories accumulated by the heat transfer fluid after the heat exchange taking place with the fourth heat exchanger, while the second section is dedicated to heating the air flow. interior via the second heat exchanger.

The second section may optionally include an electric heating element upstream of the second heat exchanger. The electric heating element allows an additional temperature rise in the event that the heat transfer fluid is at an insufficient temperature to guarantee optimal heating of the interior air flow during the heat exchange carried out within the second heat exchanger.

According to a characteristic of the invention, the second heat transfer fluid circuit comprises a main path comprising the third heat exchanger and extending between a second point of divergence and a third point of divergence.

According to one characteristic of the invention, the second heat transfer fluid circuit comprises a first path beginning at the third point of divergence and ending at the second point of divergence, the first path being provided with the first additional pump and being configured to heat treat a electric motor and/or an electronic control module. During their operation, the electric motor and/or the electronic control module are liable to release heat and create overheating which may cause them to malfunction. The second circuit makes it possible to overcome this problem by cooling the electric motor and/or the electronic control module via the circulation of the heat transfer fluid initiated by the first additional pump. The heat treatment of the electric motor and/or of the electronic control module can be done for example by heat exchange. By heat treatment, it is also necessary to include the heating of the electric motor and/or of the electronic control module, for example in the event of very low ambient temperature.

After having cooled the electric motor and/or the electronic control module, the heat transfer fluid can circulate within the main path in order to discharge the calories accumulated by the heat exchange generated. The unloading of the calories can for example be done via the flow of outside air during the crossing of the heat transfer fluid within the third heat exchanger.

According to one characteristic of the invention, the second heat transfer fluid circuit comprises a second path beginning at a second point of convergence and ending at a fourth point of divergence, the second path being provided with the second additional pump and being configured to treat thermally an electrical storage module. Like the first channel, the second channel makes it possible to heat treat the electrical storage element which is also likely to release heat.

According to one characteristic of the invention, the second heat transfer fluid circuit comprises a third channel beginning at the second point of divergence and at the fourth point of divergence and ending at the second point of convergence and at a third point of convergence disposed on the first channel upstream of the first additional pump, the third path comprising a fifth heat exchanger configured to effect a heat exchange between the heat transfer fluid and a refrigerant fluid of a refrigerant circuit, the third path being configured to circulate the heat transfer fluid to the first lane and/or to the second lane. The third channel, just like the main channel, can allow the discharge of the accumulated calories, for example after cooling of the electric motor and/or of the electronic control module and/or of the electric storage element. Such an unloading of calories accumulated by the heat transfer fluid can therefore be carried out via the fifth heat exchanger where a heat exchange with the refrigerant fluid takes place. Contrary to the heat exchange carried out at the level of the fourth heat exchanger, the heat exchange carried out at the level of the fifth heat exchanger is done with the coolant at low temperature. It is therefore the refrigerant fluid that cools the heat transfer fluid. At the outlet of the fifth heat exchanger, the cold heat transfer fluid can be directed to the first channel and/or the second channel to cool the electric motor and/or the electronic control module and/or the electrical storage element.

According to one characteristic of the invention, the second heat transfer fluid circuit comprises a fourth channel beginning at the third point of divergence and at the fourth point of divergence and ending at the second point of convergence and at the third point of convergence, the fourth channel comprising a sixth heat exchanger, configured to effect a heat exchange between the heat transfer fluid and the external air flow and arranged upstream of the first heat exchanger and of the third heat exchanger with respect to the external air flow, the fourth path being configured to circulating the heat transfer fluid to the first channel and/or to the second channel. The fourth way makes it possible, for example, to provide additional cooling if the electric motor and/or the electronic control module and/or the electrical storage element if the heat transfer fluid is not sufficiently cooled.

The invention also covers a heat treatment system for a vehicle comprising at least one heat treatment device as described previously, and a refrigerant circuit comprising at least one compression device, a first heat exchanger configured to operate a heat exchange between the refrigerant fluid and the exterior air flow and a second heat exchanger configured to effect a heat exchange between the refrigerant fluid and the interior air flow.

The compression device makes it possible to circulate the refrigerant fluid and to increase its pressure and temperature. The first heat exchanger allows the exchange of heat between the refrigerant fluid and the outside air flow. As such, the first heat exchanger is placed within the vehicle so as to be traversed by the flow of outside air, for example at the level of the front face of the vehicle. The first heat exchanger can behave as a condenser or as an evaporator depending on an operating mode of the heat treatment system. The refrigerant can for example be a fluid of the R134a or R1234yf type, or even carbon dioxide.

The refrigerant passing through the second heat exchanger interacts with the interior air flow in order to cool the vehicle cabin. As such, just as for the second heat exchanger, the second heat exchanger can be integrated within the ventilation, heating and/or air conditioning installation mentioned above.

According to one characteristic of the invention, the refrigerant circuit comprises a third heat exchanger arranged downstream of the first heat exchanger with respect to the refrigerant fluid and installed upstream of the first heat exchanger with respect to the flow of outside air. This third heat exchanger is therefore also arranged within the path of the flow of outside air, therefore at the level of the front face of the vehicle according to the example presented above.

According to one characteristic of the invention, the refrigerant circuit comprises a first expansion member disposed upstream of the second heat exchanger and a second expansion member disposed upstream of the first heat exchanger. The expansion devices allow the expansion of the refrigerant fluid in order to lower the temperature thereof before it passes through the heat exchangers arranged downstream of said expansion devices. This is particularly the case upstream of the first heat exchanger in order for example to cool the flow of outside air upstream of the first heat exchanger and of the third heat exchanger, or upstream of the second heat exchanger so that the cold refrigerant can cool the interior air flow, for example with a view to air-conditioning the passenger compartment of the vehicle.

According to one characteristic of the invention, the fourth heat exchanger is arranged within the refrigerant circuit, between the compression device and the first heat exchanger. The heat exchange occurring within the fourth heat exchanger is carried out after the refrigerant fluid is compressed at very high pressure and temperature by the compression device. The refrigerant fluid is therefore subsequently cooled and condensed by the heat transfer fluid within the fourth heat exchanger.

According to one characteristic of the invention, the refrigerant circuit comprises a main branch which begins in a first convergence zone and which ends in a first divergence zone, and which comprises an accumulation device, the compression device, the fourth heat exchanger and the first heat exchanger. The accumulation device is arranged upstream of the compression device with respect to the direction of circulation of the refrigerant fluid. The accumulation device is a storage device for the circulating mass of the refrigerant fluid. The presence of the accumulation device also makes it possible to prevent the refrigerant fluid in liquid form from entering the compression device and damaging the latter.

The first divergence zone makes it possible to divide the main branch into at least two branches, each of the two branches ensuring a function linked to the heat treatment system, for example by passing the refrigerant fluid through a heat exchanger or by bypassing the refrigerant fluid around said heat exchanger. The first convergence zone makes it possible to group all the branches started by any zone of divergence, here the first zone of divergence.

According to one characteristic of the invention, the first divergence zone is arranged between the first heat exchanger and the third heat exchanger, the refrigerant circuit comprising a first branch which begins at the first divergence zone and which ends at the first convergence zone, the first branch comprising the third heat exchanger and the second heat exchanger. In other words, if the objective is to supply the second heat exchanger in order to air-condition the passenger compartment of the vehicle, the refrigerant fluid must circulate at least within the first branch of the first circuit.

According to one characteristic of the invention, the first circuit comprises a second branch which begins at the first divergence zone and which ends at the first convergence zone, the second branch being arranged in parallel with the first branch. The second branch joins the main branch bypassing the third heat exchanger and the second heat exchanger. This second branch thus makes it possible to circulate the refrigerant fluid when it is not necessary, for example, to cool the interior air flow.

According to one characteristic of the invention, the refrigerant circuit comprises an internal heat exchanger configured to effect a heat exchange between the refrigerant fluid circulating in the main branch and the refrigerant fluid circulating in the first branch. The internal heat exchanger comprises a first pass interposed between the accumulation device and the compression device at the level of the main branch, and a second pass arranged between the third heat exchanger and the second heat exchanger. The internal heat exchanger improves the coefficient of performance of the refrigerant circuit.

According to one characteristic of the invention, the first branch comprises a second divergence zone arranged upstream of the second heat exchanger, the refrigerant circuit comprising a third branch which begins at the second divergence zone and which ends at the first convergence zone, the third branch comprising the fifth heat exchanger, as well as an expansion device installed upstream of the fifth heat exchanger. Advantageously, the second divergence zone is also arranged downstream of the internal heat exchanger, since the refrigerant fluid circulating within the third branch may also require additional cooling before circulating therein.

As described above, the fifth heat exchanger guarantees an exchange of heat between the refrigerant fluid and the heat transfer fluid. Within the fifth heat exchanger, the heat transfer fluid is cooled by the refrigerant, in order to cool the electric motor, the electronic control module or the electrical storage element. Thus, even if the need is not to cool the internal air flow, the refrigerant fluid can circulate at least partially in the first branch, then in the third branch to cool the heat transfer fluid. After passing through the fifth heat exchanger, the refrigerant fluid joins the main branch via the first convergence zone. The latter therefore allows the connection of the first branch, the second branch and the third branch to the main branch.

The expansion device is installed upstream of the fifth heat exchanger, and ensures the expansion of the refrigerant fluid in order to optimize the cooling of the heat transfer fluid.

According to one characteristic of the invention, the main branch comprises a third divergence zone arranged upstream of the second expansion device, the refrigerant circuit comprising a fourth branch which begins at the third divergence zone and which ends at a second convergence zone located on the first branch and downstream of the third heat exchanger. The fourth branch makes it possible to bypass the first heat exchanger and the third heat exchanger but nevertheless to join the first branch thereafter, upstream of the second heat exchanger. This fourth branch is for example used when the heat treatment system is in dehumidification mode, which dehumidifies the air present in the passenger compartment of the vehicle, by cooling the interior air flow via the second heat exchanger, then by heating the interior air flow via the second heat exchanger.

According to one characteristic of the invention, the refrigerant circuit comprises a first valve arranged on the second branch and a second valve arranged on the fourth branch, the first heat exchanger and the second heat exchanger being traversed in series by the fluid refrigerant when the first valve and the second valve are in the closed position, the first heat exchanger and the second heat exchanger being traversed in parallel by the refrigerant fluid when the first valve and the second valve are in the open position. The valves make it possible to authorize or prohibit the circulation of the refrigerant fluid in the second branch and/or in the fourth branch. Thus, if the two valves are closed, the refrigerant fluid necessarily circulates in the first branch, and therefore through the first heat exchanger, the third heat exchanger and the second heat exchanger in series. When the two valves are open, the refrigerant circulates in parallel in the second branch and in the fourth branch.

Other characteristics and advantages of the invention will become apparent through the description which follows on the one hand, and several embodiments given by way of indication and not limiting with reference to the appended diagrammatic drawings on the other hand, on which :

represents a heat treatment device according to the invention,

represents a direction of circulation of a heat transfer fluid circulating in the heat treatment device according to a first mode of operation,

represents a direction of circulation of the heat transfer fluid circulating in the heat treatment device according to a second mode of operation,

represents a direction of circulation of the heat transfer fluid circulating in the heat treatment device according to a third mode of operation,

represents a heat treatment system for a vehicle, integrating a refrigerant circuit and a heat treatment device according to the invention.

The terms upstream and downstream used in the following description refer to the direction of circulation of the fluid considered, that is to say the heat transfer fluid, a flow of air outside 5 of a passenger compartment of the vehicle and/or a flow of interior air 6 sent to the passenger compartment of the vehicle.

In FIGS. 2 to 4, the portions traversed by the heat transfer fluid are in solid lines and the portions without circulation of fluid are in dotted lines. Furthermore, the circulation of heat transfer fluid is illustrated by indicating its direction of circulation by arrows. On the , a refrigerant circuit 2 is shown in solid lines while a heat treatment device 3 is shown in phantom.

The terms "first", "first", "second", etc. used in the description are not intended to indicate a level of hierarchy or order the elements they accompany. These terms make it possible to distinguish the elements that they accompany and can be interchanged without reducing the scope of the invention.

There illustrates a heat treatment device 3 according to the invention, integrated within a vehicle and configured to allow the circulation of a heat transfer fluid. By way of example, the heat transfer fluid circulating within the heat treatment device 3 can for example be glycol water.

The heat treatment device 3 is divided into a first circuit 301 of heat transfer fluid and a second circuit 302 of heat transfer fluid. The first circuit 301 and the second circuit 302 are not communicating with each other.

The first circuit 301 comprises a first heat exchanger 50 configured to effect a heat exchange between the coolant and a flow of air 5 outside a passenger compartment of the vehicle. In order to be able to interact with the flow of outside air 5, the first heat exchanger 50 can for example be positioned on the front face of the vehicle. The first heat exchanger 50 comprises an inlet 501 and an outlet 502. It is understood that when the heat transfer fluid is in circulation and passes through the first exchanger 50, the heat transfer fluid enters through the inlet 501 and exits through the outlet mouth 502.

The first circuit 301 also includes a second heat exchanger 55 configured to perform a heat exchange between the heat transfer fluid and an interior air flow 6 sent to the passenger compartment of the vehicle. The second heat exchanger 55 therefore makes it possible to heat the interior air flow 6 so that the latter is sent into the passenger compartment to heat it. As such, the second heat exchanger 55 can for example be integrated within a ventilation, heating and/or air conditioning installation 4.

The second circuit 302 is for its part dedicated to heat treatment of an electric motor 7 and/or of an electronic control module 8 and/or of an electrical storage element 9. By heat treatment, it is necessary to understand a cooling of the aforementioned elements which are likely to give off heat when they are in operation, but also potentially heating of these same elements, for example in the event of extremely low ambient temperature.

In order to participate in the heat treatment of the electric motor 7 and/or of the electronic control module 8 and/or of the electric storage element 9, the second circuit comprises in particular a third heat exchanger 58. Just as for the first heat exchanger 50 , the third heat exchanger 58 is configured to perform a heat exchange between the heat transfer fluid and the outside air flow 5. The third heat exchanger 58 is therefore arranged so as to be at the level of a path of the air flow exterior 5, in the same way as the first heat exchanger 50. The third heat exchanger 58 comprises an inlet 581 and an outlet 582. The heat transfer fluid, when the latter is in circulation within the second circuit 302 and passes through third heat exchanger 58, enters through inlet 581 and exits through outlet 582.

Within the heat treatment device 3 according to the invention, the first heat exchanger 50 and the third heat exchanger 58 are arranged side by side, so that their respective planes of elongation coincide with each other. Such a configuration makes it possible to have independence between the first circuit 301 and the second circuit 302. In other words, the heat transfer fluid cannot flow from the first circuit 301 to the second circuit 302 and vice versa. This also means that the inlet mouth 501 and the inlet orifice 581, as well as the outlet mouth 502 and the outlet orifice 582 are distinct from each other.

On the , the elongation planes of the first heat exchanger 50 and of the third heat exchanger 58 coincide, but it is possible that these same elongation planes are simply parallel to each other without being coincident. The first heat exchanger 50 and the third heat exchanger 58 can also be substantially parallel to each other at +/- 2°. The first heat exchanger 50 and the third heat exchanger 58 are moreover not superposed with respect to a direction of the flow of outside air 5. In other words, a portion of the flow of outside air 5 crossing the first heat exchanger 50 does not cross not the third heat exchanger 58 and vice versa. The heat treatment device 3 according to the invention therefore differs from a heat treatment device comprising a single heat exchanger instead of the first heat exchanger 50 and the third heat exchanger 58, and which therefore implies that at least one portion of the heat treatment device is common to the first circuit 301 and to the second circuit 302.

The first heat exchanger 50 and the third heat exchanger 58 can be two independent exchangers with respect to each other, or else can form a one-piece assembly comprising a junction separating the first heat exchanger 50 and the third heat exchanger 58.

To go into more detail as to the structure of the first circuit 301 and of the second circuit 302, the first circuit 301 comprises a main section 30 extending between a first point of convergence 91 and a first point of divergence 81. From the first point of divergence 81, the first circuit 301 divides into a first section 31 and a second section 32, each extending to the first point of convergence 91.

The main section 30 comprises a main pump 71 ensuring the circulation of the heat transfer fluid within the first circuit 301. The main section 30 also comprises a fourth heat exchanger 56 configured to perform a heat exchange with a refrigerant of a circuit of refrigerant fluid 2. The heat exchange operated by the fourth heat exchanger 56 makes it possible to pre-cool the compressed refrigerant fluid upstream of the fourth heat exchanger as will be detailed later. The fourth heat exchanger 56 also makes it possible to preheat the coolant in a potential optical heating of the passenger compartment of the vehicle thereafter. The main section 30 extends as far as the first point of divergence 81. A first three-way valve 75 can for example be arranged at the level of the first point of divergence and be remotely controlled in order to direct the heat transfer fluid towards the first section 31 and/or to the second section 32 as needed.

The first section 31 of the first circuit 301 is the section which leads the heat transfer fluid to the first heat exchanger 50, then to the first point of convergence 91. The circulation of the heat transfer fluid within the first heat exchanger 50 allows for example a discharging the calories of the heat transfer fluid by the external air flow 5, and this in order to participate again in the pre-cooling of the refrigerant fluid when the heat transfer fluid again passes through the fourth heat exchanger 56.

The second section 32 includes the second heat exchanger 55 which ensures the heating of the interior air flow 6 which can then heat the passenger compartment of the vehicle thereafter. The passage of the heat transfer fluid through the fourth heat exchanger 56 therefore makes it possible to ensure heating of the heat transfer fluid which is then capable of heating the interior air flow 6 during the passage within the second heat exchanger 55. In the case where the heat transfer fluid has not been sufficiently heated within the fourth heat exchanger 56, the second section 32 comprises an electric heating element 74, arranged within the second section 32, upstream of the second heat exchanger 55, and allowing a additional heating of the heat transfer medium. Downstream, from the second heat exchanger 55, the second section 32 extends until it joins the first convergence point 91.

The second circuit 302, configured to thermally treat the electric motor 7 and/or the electronic control module 8 and/or the electrical storage element 9, comprises a main path 33 including the third heat exchanger 58. The second circuit 302 comprises also a first channel 34 within which the heat treatment of the electric motor 7 and of the electronic control module 8 takes place, and a second channel 35 within which the heat treatment of the thermal storage element 9 takes place .

The main path 33 extends between a second point of divergence 82 to a third point of divergence 83. The first path 34 extends for its part from the third point of divergence 83 to the second point of divergence 82. distribution of the heat transfer fluid taking place at the level of the third point of divergence 83 is for example controlled by a second three-way valve 76, and the distribution of the heat transfer fluid taking place at the level of the second point of divergence 82 is for example controlled by a third three-way valve 77.

The circulation of the heat transfer fluid in particular at the level of the first channel 34 is initiated by a first additional pump 72 placed on the first channel 34. The heat transfer fluid circulating in the first channel 34 interacts with the electronic control module 8 and with the electric motor 7 in order to heat treat them. Such heat treatment can be done for example by heat exchange via a heat exchanger, not shown. The first channel 34 is then extended to the second point of divergence 82, where the heat transfer fluid can flow towards the main channel 33, for example to discharge calories within the third heat exchanger 58 after having cooled the engine. electric 7 and the electronic control module 8.

At the second point of divergence 82, and depending on the active mode of operation, the heat transfer fluid can also flow towards a third channel 36. The third channel 36 allows additional cooling of the heat transfer fluid due to the presence of a fifth heat exchanger 57. The fifth heat exchanger 57, like the fourth heat exchanger 56, is configured to perform a heat exchange with the refrigerant of the refrigerant circuit 2. The refrigerant circulating through the fifth heat exchanger 57 is at low temperature and allows therefore the cooling of the heat transfer fluid, for example after the latter has cooled the electric motor 7 and the electronic control module 8. After having passed through the fifth heat exchanger 35, the heat transfer fluid can circulate to a second point convergence 92 which constitutes the starting point of the second channel 35, or up to a third point t convergence 93, which is disposed at the level of the first channel 34, upstream of the first additional pump. The third channel 36 therefore makes it possible to cool the heat transfer fluid and to circulate it to the first channel 34 and/or the second channel 35 according to the need for cooling of the electric motor 7, of the electronic control module 8 or of the electrical storage element 9. The third channel 36 includes a first non-return valve 79 so that the heat transfer fluid passing through the third point of convergence 93 does not engage towards the third channel 36.

The second channel 35 includes a second additional pump 73 also allowing the circulation of the heat transfer fluid. The presence of two pumps within the second circuit 302 is necessary in order to circulate the heat transfer fluid according to all the different operating modes detailed below. The heat treatment of the electrical storage element 9 by the heat transfer fluid can for example be done by means of a heat exchanger, not shown. The second channel 35 continues up to a fourth point of divergence 84. The latter can for example comprise a fourth three-way valve 78, which in particular makes it possible to circulate the heat transfer fluid coming from the second channel 35 towards the third channel 36, so that the heat transfer fluid is cooled via the fifth heat exchanger 57.

The second circuit 302 finally comprises a fourth channel 37. The fourth channel 37 begins at the level of the third point of divergence 83, but also at the level of the fourth point of divergence 84. Thus, the heat transfer fluid coming from the main channel 33 and the fluid coolant from the second channel 35 can be directed to the fourth channel 37. It should be noted that the fourth channel 37 includes a second non-return valve 70 so that the heat transfer fluid entering the fourth channel 37 from the fourth point of divergence 84 does not flow towards the third point of divergence 83.

The fourth channel 37 comprises a sixth heat exchanger 59, which is also arranged to effect a heat exchange with the outside air flow 5. The sixth heat exchanger 59 is arranged upstream of the first heat exchanger 50 and of the third heat exchanger thermal 58 with respect to the direction of circulation of the flow of outside air 5. The fourth channel 37 thus allows additional cooling of the heat transfer fluid if necessary. At the outlet of the sixth heat exchanger 59, the heat transfer fluid can circulate up to the second point of convergence 92 and/or up to the third point of convergence 93 in order to circulate respectively within the second channel 35 or the first channel 34 and to provide a supply of cooled heat transfer fluid.

There represents the circulation of the heat transfer fluid within the heat treatment device 3 according to a first mode of operation. The purpose of this first mode of operation is to guarantee cooling of the electric motor 7, of the electronic control module 8 and of the electric storage element 9, while acting on the refrigerant of the refrigerant circuit 2 so that the latter can, for example, cool the vehicle interior via the ventilation, heating and/or air conditioning system 4.

To do this, the initiation of the circulation of the heat transfer fluid within the first circuit 301 is initiated by the main pump 71. Within the main section 30, the heat transfer fluid circulates in order through the main pump 71 and the fourth heat exchanger 56 in order to pre-cool the refrigerant fluid also circulating through the fourth heat exchanger 56, the refrigerant fluid being at this stage at high temperature. Subsequently, the heat transfer fluid reaches the first point of divergence, where the first three-way valve 75 only authorizes the circulation of the heat transfer fluid within the first section 31. The heat transfer fluid thus circulates as far as the first heat exchanger 50 by entering it via the inlet mouth 501 and leaving it via the outlet mouth 502. Thanks to the heat exchange operated between the flow of outside air 5 and the heat transfer fluid circulating within the first heat exchanger 50 , the heat of the heat transfer fluid stored after the heat exchange carried out with the refrigerant within the fourth heat exchanger 56 is dissipated in the flow of outside air 5. The heat transfer fluid, at the outlet of the first heat exchanger 50, can thus join the main section 30 via the first convergence point 91, in order to cool the refrigerant fluid again via the fourth heat exchanger 56.

The circulation of the heat transfer fluid within the second circuit 302 is for its part divided into two loops. A first loop is dedicated to cooling the electric motor 7 and the electronic control module 8, while a second loop is dedicated to cooling the electrical storage element 9.

The circulation of the heat transfer fluid within the first loop takes place exclusively within the main channel 33 and the first channel 34. The circulation of the heat transfer fluid at the level of the first loop is initiated by the first additional pump 72. The fluid Heat carrier therefore circulates within the first channel 34 and cools the electronic control module 8, then the electric motor 7, which are both capable of giving off heat during their operation. The calories are thus recovered by the heat transfer fluid. The heat transfer fluid then circulates as far as the second point of divergence 82, where the third three-way valve 77 directs the heat transfer fluid exclusively towards the main channel 33. Within the latter, the heat transfer fluid passes through the third heat exchanger 58 by entering via the inlet 581 and leaving through the outlet 582. Thanks to the heat exchange between the external air flow 5 and the heat transfer fluid circulating within the third heat exchanger 58, the heat of the heat transfer fluid stored after the heat exchange performed with the electronic control module 8 and the electric motor 7 is dissipated in the external air flow 5. At the outlet of the third heat exchanger 58, the heat transfer fluid circulates to the third point divergence 83, where the second three-way valve 76 directs the heat transfer fluid exclusively to the first channel 34 so that the latter can again cool the electronic control module electronics 8 and the electric motor 7.

The second loop of heat transfer fluid formed within the second circuit 302 has the function of cooling the electrical storage element 9. The heat transfer fluid circulating along the second loop is therefore driven within the second path 35 by the second additional pump 73 and therefore makes it possible to cool the electrical storage element 9 by capturing the heat from the latter. The heat transfer fluid heated by the heat exchange with the electrical storage element 9 then circulates to the fourth point of divergence 84 where the fourth three-way valve 78 directs it exclusively within the third way 36. The fluid coolant is then cooled by crossing the fifth heat exchanger 57, thanks to the heat exchange carried out with the cold refrigerant of the refrigerant circuit 2. At the outlet of the fifth heat exchanger 57, the cold heat transfer fluid circulates up to the second point convergence 92 in order to join the second channel 35 upstream of the second additional pump 73. The calories generated by the electrical storage element 9 are thus regularly captured by the heat transfer fluid which thus protects the electrical storage element 9 from potential overheating.

There represents the circulation of the heat transfer fluid within the heat treatment device 3 according to a second mode of operation. The latter is similar to the first mode of operation except that the flow of outside air 5 does not sufficiently dissipate the calories stored by the heat transfer fluid when the latter passes through the third heat exchanger 58, and that it is therefore necessary to generate additional cooling of the heat transfer fluid.

To do this, at the outlet of the third heat exchanger 58, instead of directing all of the heat transfer fluid to the first channel 34, the second three-way valve 76 will direct a first fraction of heat transfer fluid to the first channel 34 such that is represented on the , and a second fraction of heat transfer fluid to the fourth channel 37. The heat transfer fluid circulating in the fourth channel 37 then passes through the sixth heat exchanger 59 where the flow of outside air 5 passes through upstream of the third heat exchanger 58. Once the cooling of the second fraction of heat transfer fluid via the sixth heat exchanger 59 carried out, the latter then circulates to the third point of convergence in order to join the first channel 34.

The circulation of the heat transfer fluid within the fourth channel 37 thus provides additional cooling of the electric motor 7 and/or of the electronic control module 8. It should be noted that the heat transfer fluid at the outlet of the sixth heat exchanger 59 can also reach the second channel 35 in the case where it is the electrical storage element 9 which requires more intense cooling.

The circulation of heat transfer fluid being, with the exception of what has just been described, identical to the circulation of heat transfer fluid illustrated within the , reference will be made to the description of the latter for the details concerning said circulation.

There represents the circulation of the heat transfer fluid within the heat treatment device 3 according to a third mode of operation. The third mode of operation consists in participating in the heating of the passenger compartment of the vehicle via the first circuit 301 while cooling the electric motor 7 and the electronic control module 8 via the second circuit 302.

At the level of the first circuit 301, the circulation of the heat transfer fluid is again initiated by the main pump 71. The heat transfer fluid circulates within the main section 30, being heated by the heat exchange occurring at the level of the fourth exchanger thermal 56, and this while pre-cooling the refrigerant on the other hand. After being heated, the heat transfer fluid circulates to the first point of divergence 81, where the first three-way valve 75 redirects the heat transfer fluid exclusively within the second section 32. At this point, it can then be heated additionally. by the electric heating element 74 if the heat exchange via the fourth heat exchanger 56 has increased the temperature of the heat transfer fluid insufficiently. This being done, the heat transfer fluid circulates at high temperature through the second heat exchanger 55 in order to effect a heat exchange with the internal air flow 6 before joining the main section 30 upstream of the main pump 71, and this via the first point of convergence 91. The heat transfer fluid is thus placed at high temperature in order to heat the interior air flow 6, the latter thus making it possible to heat the passenger compartment of the vehicle.

In this third mode of operation, at the level of the second circuit 302, the heat transfer fluid circulates according to a loop guaranteeing the cooling of the electric motor 7 and of the electronic control module 8. The heat transfer fluid is thus driven within the first channel 34 in order to to cool the electronic control module 8, then the electric motor 7 in a manner similar to what has been described previously. The fluid then circulates to the second point of divergence 82, where the third three-way valve 77 which will direct the heat transfer fluid within the third channel 36. The heat transfer fluid, heated following the cooling of the electronic control module 8 and the electric motor 7, is then cooled within the fifth heat exchanger 57 by the refrigerant fluid circulating within the refrigerant circuit 2. Once out of the fifth heat exchanger 57, the cooled heat transfer fluid circulates until it reaches the first path 34 , upstream of the first additional pump 72.

There represents a heat treatment system 1 for a vehicle comprising the refrigerant circuit 2 mentioned above, as well as the heat treatment device 3. On this , the heat treatment device 3 shown in phantom is identical to that described in the preceding figures and reference will therefore be made to the description of the concerning the structural and functional properties of the heat treatment device 3. The following description therefore presents an example of a refrigerant circuit 2 compatible for interacting with the heat treatment device 3, and makes it possible to better understand said interactions between the circuit refrigerant fluid 2 and the heat treatment device 3. For reasons of clarity, the external air flow 5 is not illustrated as passing through all of the exchangers interacting therewith, but the external air flow 5 interacts well with all these exchangers.

The refrigerant fluid circuit 2 is configured to allow the circulation of the refrigerant fluid which can for example be a fluid of the R134a or R1234yf type.

The refrigerant circuit 2 comprises a plurality of branches forming a closed circuit. The refrigerant circuit 2 notably comprises a main branch 20 which begins in a first convergence zone 28 and which ends in a first divergence zone 25. The refrigerant fluid circulates within the main branch 20 of the first convergence zone 28 towards the first zone of divergence 25. The main branch 20 comprises in particular a compression device 61 and a first heat exchanger 51.

The compression device 61 ensures the circulation of the refrigerant fluid within the refrigerant circuit 2 and the high pressure and high temperature setting of said refrigerant fluid.

The first heat exchanger 51 is configured to perform a heat exchange with the outside air flow 5 and must therefore be positioned so as to be at the level of the path of said outside air flow 5. As such, at the Like the first heat exchanger 50 and the third heat exchanger 58, the first heat exchanger 51 can for example be positioned at the front face of the vehicle. The first heat exchanger 51 can act as a condenser or an evaporator depending on the role of the refrigerant circuit 2. The first heat exchanger 51 is arranged upstream of the first heat exchanger 50 and the third heat exchanger 58 with respect to the direction of circulation of the outside air flow 5, and downstream of the sixth heat exchanger 59.

The first zone of divergence 25 is located downstream of the first heat exchanger 51 and allows the separation of the main branch 20 into a first branch 21 and into a second branch 22. The first branch 21 notably comprises a second heat exchanger 52 which can for example be arranged, like the second heat exchanger 55, within the ventilation, heating and/or air conditioning installation 4. The second heat exchanger 52 is configured to take part in the air conditioning function of the vehicle thanks to a heat exchange with the internal air flow 6. In order to improve the cooling capacity of the second heat exchanger 52, the first branch 21 comprises a first expansion member 63 making it possible to lower the pressure of the refrigerant fluid before its entry into the second heat exchanger 52.

The main branch 20 makes it possible to circulate the refrigerant fluid through the fourth heat exchanger 56 described above. The fourth heat exchanger 56 is arranged downstream of the compression device 61. The latter compresses the refrigerant fluid which then passes through the fourth heat exchanger at very high temperature and is thus cooled and condensed by the heat transfer fluid as described above.

After pre-cooling via the fourth heat exchanger 56, the refrigerant circulates in the main branch 20 as far as the first heat exchanger 51. The main branch 20 comprises a second expansion device 64 upstream of the first heat exchanger 51 and in downstream of the fourth heat exchanger 56. The second expansion member 64 can provide pre-expansion of the refrigerant fluid before it passes through the first heat exchanger 51. Depending on an operating mode of the heat treatment system 1, the heat exchange which takes place within the first heat exchanger 51 between the refrigerant fluid and the outside air flow 5 can make it possible either to cool the refrigerant fluid, or to cool the outside air flow so that the latter reaches at the level of the first heat exchanger 50 and the third heat exchanger 58 at lower temperature, for example with the aim of favoring the maximum capture of calories from the f coolant fluid circulating within the first heat exchanger 50 or the third heat exchanger 58.

At the outlet of the first heat exchanger 51, the refrigerant fluid circulates as far as the first divergence zone 25 and can then circulate within the first branch 21 or the second branch 22 according to need. As such, the second branch 22 comprises a first valve 66 which, in the open position, allows the circulation of the refrigerant fluid within the second branch 22. In this situation, the refrigerant fluid then circulates as far as the first convergence zone 28 and thus joins the main branch 20.

If the first valve 66 is in the closed position, the refrigerant fluid can only circulate within the first branch 21. The refrigerant fluid then passes through a third heat exchanger 53, arranged upstream of the first heat exchanger 51 with respect to the direction circulation of the outside air flow 5. The third heat exchanger 53 acts as a sub-cooler, and guarantees significant cooling of the refrigerant fluid by its positioning upstream of the first heat exchanger 51 with respect to the air flow outside 5.

The refrigerant fluid, at the outlet of the third heat exchanger 53 circulates within the first branch 21 as far as a second divergence zone 26. The second divergence zone 26 allows the refrigerant fluid to continue its circulation within the first branch 21 and/or to circulate within a third branch 23 of the refrigerant circuit 2.

The first branch 21 continues up to the first expansion device 63 then to the second heat exchanger 52 mentioned above and guaranteeing the cooling operation of the interior air flow 6 within the ventilation, heating and/or installation. or air conditioning 4. The first branch 21 then ends at the level of the first convergence zone 28, thus joining the main branch 20.

The third branch 23 begins at the second zone of divergence 26 and ends at the first zone of convergence 28, and includes the fifth heat exchanger 57 mentioned above. The third branch 23 is thus put in place with the aim of discharging the heat from the heat transfer fluid, as has been described in FIGS. 2 to 4. In order to optimize the pressure of the refrigerant fluid, the third branch 23 comprises a expansion device 65, upstream of the fifth heat exchanger 57. The refrigerant fluid, after having passed through the fifth heat exchanger 57 subsequently joins the main branch 20 via the first convergence zone 28. The latter therefore allows the junction of the first branch 21, from the second branch 22 and from the third branch 23 to the main branch 20.

The main branch 20 also includes an accumulation device 62, downstream of the first convergence zone 28 and upstream of the compression device 61. The accumulation device 62 makes it possible to recover the refrigerant fluid from the first branch 21, of the second branch 22 and of the third branch 23 and to keep a potential fraction of coolant fluid in liquid form so that said fraction does not continue its circulation within the main branch 20 and does not damage the compression device 61 by traversing this one.

The refrigerant circuit 2 also comprises an internal heat exchanger 54 arranged downstream of the accumulation device 62 and upstream of the compression device 61 at the level of the main branch 20, and downstream of the third heat exchanger 53 and upstream of the second zone of divergence 26 at the level of the first branch 21. The heat exchange operated by the internal heat exchanger 54 makes it possible to optimize the cooling of the refrigerant fluid circulating within the first branch 21.

Finally, the refrigerant circuit 2 comprises a fourth branch 24 arranged between a third zone of divergence 27 and a second zone of convergence 29. The third zone of divergence 27 is arranged at the level of the main branch 20, downstream of the fourth exchanger 56 and upstream of the second expansion member 64. The second convergence zone 29 is arranged at the level of the first branch, downstream of the third heat exchanger 53 and upstream of the internal heat exchanger 54. The fourth branch 24 therefore makes it possible to join the main branch 20 to the first branch 21 without passing through the first heat exchanger 51 and the third heat exchanger 53. Circulating the refrigerant fluid via the fourth branch 24 makes it possible, for example, to implement a dehumidification mode consisting of cooling and then heating the interior air flow 6 respectively via the second heat exchanger 52 and the second exchanger t hermic 55. The circulation of the refrigerant fluid within the fourth branch 24 is managed by a second valve 67.

In order to avoid circulation of the refrigerant fluid in the opposite direction at the outlet of the fourth branch 24, that is to say in a direction of circulation going from the second convergence zone 29 towards the third heat exchanger 53, the first branch 21 comprises a third non-return valve 68 downstream of the third heat exchanger 53 and upstream of the second convergence zone 29.

Of course, the invention is not limited to the examples which have just been described and many adjustments can be made to these examples without departing from the scope of the invention.

The invention, as it has just been described, achieves the goal it had set itself, and makes it possible to propose a heat treatment device making it possible to form two distinct heat transfer fluid circuits. Variants not described here could be implemented without departing from the context of the invention, provided that, in accordance with the invention, they comprise a heat treatment device in accordance with the invention.

Claims (12)

Heat treatment device (3) for a vehicle, comprising at least a first heat transfer fluid circuit (301) and a second heat transfer fluid circuit (302), the first heat transfer fluid circuit (301) comprising a main pump (71), a first heat exchanger (50) configured to effect a heat exchange between the coolant and a flow of air (5) exterior to a passenger compartment of the vehicle, and a second heat exchanger (55) configured to effect a heat exchange between the heat transfer fluid and an interior air flow (6) intended to be sent to the passenger compartment of the vehicle, the second heat transfer fluid circuit (302) comprising at least one first additional pump (72), at least one second additional pump (73), and a third heat exchanger (58) configured to effect a heat exchange between the heat transfer fluid and the external air flow (5), characterized in that the first heat exchanger (50) and the third heat exchanger thermal eur (58) are side by side and extend in elongation planes intended to be crossed by the external air flow (5), said elongation planes being parallel to each other at +/- 2°. Heat treatment device (3) according to Claim 1, in which the planes of elongation of the first heat exchanger (50) and of the third heat exchanger (58) coincide. Heat treatment device (3) according to Claim 1 or 2, in which the first heat exchanger (50) and the third heat exchanger (58) form a single unit. Heat treatment device (3) according to any one of the preceding claims, in which the first heat exchanger (50) comprises an inlet (501) and an outlet (502) and the third heat exchanger (58) comprises an inlet (581) and an outlet (582), the inlet (501) being separate from the inlet (581) and the outlet (502) being separate from the outlet port (582). Heat treatment device (3) according to any one of the preceding claims, in which the first heat transfer fluid circuit (301) comprises a main section (30) beginning at a first point of convergence (91) and ending at a first point of divergence (81), as well as a first section (31) and a second section (32) which both start at the first point of divergence (81) and end at the first point of convergence (91). Heat treatment device (3) according to the preceding claim, in which the main section (30) comprises the main pump (71) and a fourth heat exchanger (56) configured to operate a heat exchange between the heat transfer fluid and a refrigerant of a refrigerant circuit (2). Heat treatment device (3) according to claim 5 or 6, wherein the first section (31) comprises the first heat exchanger (50), the second section (32) comprising the second heat exchanger (55). Heat treatment device (3) according to any one of the preceding claims, in which the second heat transfer fluid circuit (302) comprises a main path (33) comprising the third heat exchanger (58) and extending between a second point of divergence (82) and a third point of divergence (83). Heat treatment device (3) according to the preceding claim, in which the second heat transfer fluid circuit (302) comprises a first path (34) starting at the third point of divergence (83) and ending at the second point of divergence (82) , the first channel (34) being provided with the first additional pump (72) and being configured to thermally treat an electric motor (7) and/or an electronic control module (8). Heat treatment device (3) according to the preceding claim, in which the second heat transfer fluid circuit (302) comprises a second path (35) starting at a second point of convergence (92) and ending at a fourth point of divergence ( 84), the second path (35) being provided with the second additional pump (73) and being configured to heat treat an electrical storage module (9). Heat treatment system (1) of a vehicle comprising at least one heat treatment device (3) according to any one of the preceding claims, and a refrigerant circuit (2) comprising at least one compression device (61) , a first heat exchanger (51) configured to effect heat exchange between the refrigerant fluid and the outside air flow (5) and a second heat exchanger (52) configured to effect heat exchange between the refrigerant fluid and the interior air flow (6). Heat treatment system (1) according to the preceding claim, combined with claim 6, in which the fourth heat exchanger (56) is arranged within the refrigerant circuit (2), between the compression device (61) and the first heat exchanger (51).